Apparatus for controlling ring spinning machines



Nov. 14, 1933. TRIQU 1,934,999

APPARATUS FOR CONTROLLING RING SPINNING MACHINES Filed Feb. 3, 1932 4 Sheets-Sheet l I NVENTOR.

ANDRE TRlou.

ATTORNEY. 9 4241% Nov. 14, 1933. A. TRIOU 1,934,999

APPARATUS FOR CONTROLLING RING SPINNING MACHINES Filed Feb. 5, 1952 '4 Sheets-Sheet 2 /NVENTOR. ANDRE TR IOU.

ATTORNEY.

NOV. 14, 1933. A, TRIOU 1,934,999

APPARATUS FOR CONTROLLING RING SPIHNING KACHINBS Filed Feb. 5, 1952 4 Sheets-Sheet s rllI IHI INVENTOR ANDRE TRlou.

ATTORNEY.

A. TRIOU Nov. 14, 1933.

4 Sheets-Sheet 4 Filed Feb. 3, 1932 L I, w E R h 5 Z 5 5 3 R D 1Q. AN M 9 8 a 1 m J. M. a INN W v 5 J47 M ar/1mm I .J/fli. I E II Elli-H55;

ATTORNEY. -%44 Patented Nov. 14, 1933 UNITED STATES APPARATUS FOR CONTROLLING RING SPINNING MACHINES Andre Triou, Montgeron, France Application February 3, 1932, Serial No. 590,764, and in Luxembourg February 20, 1931 1 Claim.

This invention consists in an improved construction of apparatus for controlling ring spinning machines of the kind designed to allow of varying the speed of rotation of the spindles to suit the stages of winding of the cops.

The invention will be fully understood with the aid of the following description and the drawings hereunto annexed, which description and drawings are only given by way of example.

0 In the drawings:

Fig. 1 is a diagram illustrating the formation of a cop or bobbin in a spinning machine.

Figure 2 is an elevation of the mechanism of the invention.

Figure 3 is a section drawn to an enlarged scale on line 3--3 of Fig. 2.

Fig. 4 diagrammatically illustrates the modification of the mechanism in longitudinal axial section.

Figure 5 is a similar view of the mechanism in Fig. 4 in the inactive period.

Figure 6 is a partial end view.

Figure 7 diagrammatically illustrates in front elevation with part broken away, a part of a govemor for a spinning machine constructed according to the invention.

Figure 8 is a section on line 88 of Fig. 7.

With speed-changing mechanism the formation of the bobbin can be effected at different speeds according to the phases of the winding and the speeds being periodically different in each of these phases.

The spindles should rotate at the speed limit imposed, firstly by the thickness of the thread, secondly by the critical moment of formation of the heel, thirdly by the diameter of the windings, fourthly by the diameter of the balloon, which diameter decreases in proportion as the carriage rises and which renders the thread more and more liable to break especially towards the end of the take oif when the small windings of the successive cone layers reach the smallest diameter.

The output of a spinning machine not provided with speed-changing apparatus is in relation to this speed limit.

In order to increase the output of the machine, therefore, the speed limit must be increased wherever the stages of the work allow it without the risk of breaking the thread.

As can be gathered from Figure 1 the formation of a whole bobbin can be divided into three stages, heel, body and tip. A little more than one-sixth of the operation is necessary for the formation of the heel. The next four-sixths are needed for the body, and a little less than onesixth for the formation of the tip.

If we take a normal spinning machine which, with a certain size of thread can work at the speed limit of 650 revolutions per minute during so the whole of the operation, it is advantageous to periodically vary the speed of rotation of the spindle by increasing the rate from zero up to to 80 revolutions per minute and again reducing it to zero, this being effected exactly parallel with 65 the rise and descent of the carriage, this increase and decrease respectively corresponding to the formation of the conical windings of the bobbin.

The formation of the heel is usually efiected by the provision of a cam, which helps to give the 70 heel the particular shape indispensable to the good appearance of the cop at the base of the bobbin.

Experience has shown, that during the first phase relating to the formation of the heel of the bobbin the speed can be gradually raised, without increasing the risk of breakage, from 650 revolutions per minute to 700 and even 720 revolutions per minute, and that, during the second stage relating to the formation of the body, one could (still without further risk of breakage) retain this speed during the whole duration of this stage.

During the third stage corresponding to the formation of the tip of the bobbin this speed can be gradually reduced towards its starting point: that is to say towards 650 revolutions per minute (speed corresponding to the critical moments of the formation of the small windings in each of the conical parts of the bobbin). But during the whole duration of these stages, the carriage is alternately rising and descending regularly for the formation of the windings or more correctly of the cones of the windings, and the winding speed being capable of increasing from 650 to 720 revolutions per minute (speed limit for the small windings in the difierent stages) it is easily understood, that during each of the oscillations of the carriage corresponding to the formation of the cones, these speeds can be increased without further risk of breakage, when the windings increase in diameter, which movement coincides with the periodical descents of the carriage and these speeds can be resumed, when the windings decrease in diameter, which corresponds to the periodical ascents of the carriage.

With the type of thread adopted for experiment it was shown that the speed could be raised to 800 revolutions per minute and even more without further risk of breakage.

As shown in Figs. 2 and 3 a earn 1 is mounted freely rotatable on an axle 2, but can be driven in one direction by a thrust device 3, integral with a pusher-wheel 4, keyed on the axle 2.

The axle 2 is driven by a pinion 5 which is itself driven for example by means of a chain by another pinion fixed on the axle affecting the ascent and descent of the ring rail or lifter rail, the oscillations of which are combined with a general ascent.

A roller 6, mounted loosely on an axle 7, can move under the action of the cam 1.

The axle '7 can slide in a double vertical fixed slide 8, in form of a cap; and in a movable slide 9 in form of a crank, articulated on an axle 10 integral with a connecting rod 11.

The axle 7 is integral with a lever 12, articulated round an axle 13, mounted on a support capable of a translatory movement on a screw 14 of very short pitch actuated by a button 14, at the other end the lever carries at 15, a grooved pulley 16.

The connecting rod 11 slides in two fixed guides 17 and is given an alternating reciprocating movement by means of a group of articulated connecting rods and levers 18, 19 and 20.

The connecting rod 20 is articulated to a sort of pedal 21 mounted on the axle 22, which effects the oscillatory movement of the ring rail or lifter rail in its ascending and descending movements.

The lever 19 has a screw-threaded portion 23 on which are screwed two nuts 24, enabling the axle 26 to be advanced or retreated in relation to the axle to thus regulate the extent of the strokes of the connecting rod 11.

The slide 9 carries an attachment 27 to which a cable 28 is secured by one of its ends, which cable passes over the grooved pulley 16, and is secured at its other end to the lever 29, driving the change-speed gear 30.

It should be noted that the cam 1 has two inclines, one determining the increase of speed at the commencement of the ascent of the carriage, the other the decrease of speed at the end of the ascent. Preferably the mechanism is completed by a suitable brake, 'for instance a band-brake of which the drum 31 is seen, integral with the cam 1, this brake being intended to prevent the stalling of the cam 1 (due to the effect of inertia) and the passing beyond its dead point; the cam moved by the axle 2 performs a complete revolution for the complete supplying of yarn to the spindle.

The working of the mechanism is as follows:

As the winding of the bobbin proceeds the cam 1 rotates round the axle 2 raising the roller 6 and its axle 7, which rocks the articulated lever 12, raises the grooved pulley 16 and by means of the cable 28 lifts the lever 29 driving the changespeed apparatus 30 controlling the speed. The cam 1 thus subjects the speed to a first law of variation, the period of which is equal to the duration of winding of a bobbin.

On the other hand, in proportion to the rotation of the cam 1 by reason of the displacement of the axle 7, the movable slide 9 under the action of the connecting rod 11 imparts a translatory movement to its attachment 27 which undergoes a displacement increasing as the axle 7 moves away from the centre of the cam 1.

There is therefore for each stroke of the rod 11, a displacement of the attachment 27, which displacement varies with the movement of the roller 6 away from the centre of the cam 1 and which by its action on the cable 28 and the lever 29 of the change-speed gear 30, subjects the speed to a second law of variation, said variation having a period and extent variable according to the position of the cam.

It is therefore clear that by suitable adjustments effected by means of the milled button 14 and by displacing the axle 25, and by giving a suitable outline of the cam 1, the speed can be varied so that at any moment the speed required can be obtained.

I will now describe the modification illustrated in Figs. 4 to 8.

This modification is for the purpose of simplifying the construction while dispensing with the pedal on the shaft imparting the reciprocating movement to the ring rail or lifter rail, the movement corresponding to this movement being now transmitted bythe chain transmitting the movement of the axle affecting the ascent and descent of the ring rail or lifter rail the oscillations of which are combined with a general ascent to the cam axle of the governor; further the drive of the governor is effected from a point which gives the maximum of advantage. The rod 11 which slides in two fixed guides 17 is now given an alternating to and fro movement by means of the following mechanism.

A lever 32 pivotal about a fixed point 33 is articulated at 34 round a pivot fixed on the rod 11 and at 35 round a pivot fixed at the end of a rod 36.

A shell 37 connected by means of an arm 38 to the chain 39 transmitting the movement of the axle effecting the ascent and descent of the ring rail to the toothed pinion 5 is threaded on the rod 36, and owing to the balls 40 constantly driven during the working period by the spring 41 towards the conical bore 42 the shell can move in the direction of the arrow (Fig. 4) under the action of the chain 39 without moving the rod 36 while it actuates the said rod 36 when it moves in the other direction and this by reason of the pressure of the balls 40 round the rod 36.

An abutment 43 fixed on the rod 36 allows the automatic unclutching of the shell 37 when the latter is at the end of its course at the end of the rise of the ring rail.

An abutment 44 also fixed on the rod 36 allows the automatic clutching of the shell 37 (the unclutching having been produced by the abutment 43) when the latter has returned to its starting point at the time when the ring rail has returned before a fresh rise.

The operation of this mechanism differs solely from the operation of the mechanism previously described in that the reciprocating movement is obtained by means of the shell 37 fixed on the chain 39 instead of by the group comprising the pedal, rod and articulated levers.

The axle of the cam-shaft being given an oscillatory movement with a certain movement of rotation at each oscillation, the chain 36 is given an oscillatory movement with progression in the direction of the arrow (Fig. 4), for each of these oscillations there is a movement of the shell 37 in the direction contrary to the arrow which causes the lever 32 to pivot, the rod 36 being drawn in the other direction when the shell 37 no longer acts on it so that the lever 32 pivots in theother direction and the rod 11 is thus given beat movements.

Further when the shell 37 reaches the end of its course at the end of the rise of the carriage, it strikes against the abutment 43 fixed on the rod 36, the head 45 of the plunger 46 separates the two branches of the U shaped spring 47 and takes the position indicated in Fig. 5. The ring rail can then return to its starting position and displace the shell 37 (which is then in the inactive 5 period) in the direction contrary to the arrow back to its starting position, without its moving the rod 36 in its displacement. But at this moment the sleeve 48 strikes against the abutment 44 and by means of the balls 40 causes the head 45 of the plunger 46 to again separate the two branches of the spring 4'1, which will occupy the position indicated in Figure 4. The shell 37 is thus automatically replaced in the active position when it is returned to its starting point.

It can be understood that the to and fro movement is effected by the wedging action of the balls which at the correct moments clutches the rod 36 and chain 39 together.

For the purpose of rendering the curve graphically representing the speeds, more regular and consequently to make it approach as nearly as possible to the curve representing speeds giving the maximum results as shown in Figs. 7 and 8 one of the extremities of the rod 11, is articulated on the axle 49 carried by a crank 50 pivotal round the pivot 51, the other end of the rod 11 being articulated at 34 on the lever 32, and as previously described the slide 9 is articulated on the axle 49. The pivot 51 is situated at about equal distances between the extreme upper and lower positions which the axle '7 can occupy.

It can be easily understood that the axle 49 will move while describing an arc of a circle of which the centre is the centre of the pivot 51, and the attachment 27 integral with the slide 9 will not be briskly displaced to one side or the other at the end of the stroke of the rod 11 by the said slide 9 which is fixed to it which would be the case if the slide 9 is articulated on the axle 10 which has a to and fro movement.

0n the other hand it is advantageous to arrange the driving pinion of the governor on the chaincarrying cam axle driving the ring rail, this axle, normally fixed is coupled with the movement of the cams to allow the transmission to the governor, these movements being exactly those of the ring rail of the spinning machine they correspond to the phases of the spinning under consideration.

It is to be noted that the mechanisms described allow of effecting independent regulations without the necessity to stop the machine on which this mechanism is installed.

The invention is not limited to the application of the mechanism to the spinning machines as it can be applied to various other machines, neither is it limited to the details of construction describedfor instance the cam could be of any other suitable kind and the connecting rods and levers and the means connecting the cam therewith could be modified to suit particular requirements.

What I claim as my invention and desire to secure by Letters Patent of the United States 1s:-

Mechanism for obtaining variations of speed in machine having speed change gear comprising a frame, an axle mounted on said frame means for rotating said axle actuated by a moving part of the machine to which the mechanism is applied, a cam freely rotatable upon said axle, means for driving said cam in one direction only, means for preventing retrograde movement of said cam,

a second axle parallel to said first mentioned axle, a roller having its periphery resting on the periphery of said cam mounted freely on said second axle, a fixed bearing member forming a double slide within which the ends of said second axle can have vertical movement whereby said roller is guided in vertical movements imparted to it by said cam, a movable slide through which said second axle extends and can slide, a slidable rod pivoted to the upper end of said movable slide, a lever integral with said second mentioned axle, an adjustable pivot forming a fulcrum for said lever, a pulley mounted at the other end of said lever a cable passing over said pulley connected at one end to said movable slide and at the other to a lever of the speed change gear of the machine to which the mechanism is applied and lever mechanism connecting the one end of said slidable rod to a moving part of said machine to impart alternating reciprocating movements thereto.

ANDRE TRIOU. 

